Hydraulic motor gear



APT 20 1943- P. A. KlNzlE 2,317,275

HYDRAULIC MOTOR GEAR Filed June 9, 1941 2 sheets-sheet 1 INVENT OR.

BY M

ATTORNEY April 20, 1943. P. A. KlNzlE 2,317,275

HYDRAULIC MOTOR GEAR 2 Shee-ts-Sheat 2 i@ w .WY

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Filed June' 9, 1941 lill/Ill. I

Patente-cl Apr. 20, 1943 z HYDRAULIC MOTOR GEAR Phillip A. Kinzie, Denver, Colo.

Original application May 31, 1939, Serial No. 276,593. Divided and this application June 9, 1941, Serial No. 397,346

6 Claims.

The present invention is a division of my copending application, Serial No. 276,593, filed May 31, 1939.

My invention relates to hydraulic motors, and has for an object the provision of a hydraulic motor wherein fluid pressure is translated into rotary motion by means of its action on a pair of meshed gears.

Another object of my invention is to provide an improved hydraulic motor adapted for opening and closing tube valves and the like.

A further object of my invention is to provide a hydraulic motor embodying a simple and eicient arrangement of ports and control valves for supplying fluid under pressure to the set of meshed gears which translate the pressure into rotational force.

Another object of my invention is to provide a simple means for conning uid pressure to a limited area of the meshed gears, said means to comprise sealing elements at the periphery and ends of the meshed gears.

Another object of my invention is the provision of an integrally contained controlling means for directing the iiuid to the meshed gears; said means to be capable of so directing fluid flow that reversal of rotation of the meshed gearing can be effected.

Another object of my invention is the provision of a mechanical torque limiting means, said means operating in an oil bath and contained within the hydraulic motor structure.

A further object is the provision of meshing gears in the hydraulically actuated drive unit having teeth so constructed that they are individually resilient, yet relatively rigid as a unit cf the gear.

further object is to provide gear members for a hydraulically actuated drive unit, wherein the tooth elements thereof are molded of a resilient material, such as rubber, around a rigid metallic framework.

A still further object is to provide a construction of the gear mem-bers for the hydraulic motor, wherein the tooth elements thereof are molded of a resilient material, such as rubber, integrally with a rigid metallic framework, and wherein the contacting surfaces of the tooth elements are faced with metallic elements anchored in the resilient teeth.

Apparatus embodying features of my invention is illustrated in the accompanying drawings forming a part of this application, in which Fig. 1 is a plan View of my hydraulic gear motor;

Fig. 2 is a section taken on the plane II-II of Fig. 1;

Fig. 3 is a section taken on the plane III-III of Fig. 2; 5 Fig. 4 is a sectionI taken on the plane IV-IV of Fig. 2;

Fig. 5 is a section taken on the plane V-V of Fig. 2;

Fig. 6 is a section taken on the plane VI-VI 0f Fig. 2;

Fig. 7 is a section taken on the plane VII-VII of Fig. 2;

Fig. 8 is a section taken on the plane V111- VIII of Fig. '2;

Fig. 9 is a section analogous to Fig. 2, but show ing an alternate embodiment of the invention;

Fig. 10 is a section taken on the plane X-X of Fig. 9;

Fig. 11 is an enlarged fragment of Fig. 10;

Fig. 12 is a. section taken on the plane XII- XII of Fig. 11;

Fig. 13 is a section taken on the plane XIII- XII of Fig. 11; and

Fig. 14 is a fragmentary section, analogous to Fig. 11, and shows an alternate embodiment.

Referring to the drawings for a better understanding of my invention, it will become apparent that the principle of operation employed is essentially a reversal of the conditions of operation of a gear pump; that is, pressure is admitted to cause rotation of the gear units instead of rotation of the gear units being used to produce pressure.

This motor is actuated by pressure admitted through the pipe to the passageway 8l in the body 88, whence it passes into the annular space 89 surrounding the control valve 9i), which is held in tight contact with the upper liner 9| by virtue of the differential in diameters between the lower and upper portions thereof. The upper portion is provided with the seal rings 92, and the annular space 93 between the upper surface of the control valve 9i) and cover 94 is relieved to the drain through the hole 95. The upwardly extending trunnion 9E, which is sealed by the ring 91 and to which the control lever 98 is attached, provides a means for actuating the control valve 90. With the lever 98 in the position shown, pressure in the annular space 89 can not escape since no port is in communication with the triangular shaped port 99; however, when the control lever handle which is normally locked in the stop position, is unlocked and swung upright, the lever 98 can then be swung to either the .open or shut positions indicated on the top cover and dial plate |00. For the purpose of further description it will be assumed that it has been swung to the open position.

With the control valve 90 in this position, the triangular shaped port 99 will be placed in communication with a mating opening which communicates with the passageway lill. The passageway |0I will then deliver fluid under pressure to the space |02, where it will act upon the gears |03 and |04. Since there Will be in effect one tooth area upon which the fluid pressure will not be balanced. the gear |03 will rotate clockwise, and the gear |04 will rotate counterclockwise. The space |02 is sealed against pressure loss by contact with the gears of the segmental shields |05, and the upper linerl 9| and lower liner |08 in which the resistance grooves |01 are cut.

As the gears |03 and |04 rotate to the point where the lower liner- |06 no longer seals the space between the teeth on the gears, the fluid therein will ow downward into the basin space |08 formed by the bottom cover |09, and will be delivered to the drain pipe ||0 through the port The rotational force imparted on the gear |03, which has its shaft ||2 journalled in the bushings ||3 will be transmitted to'the gear |04 through the meshed teeth on gears |03 and |04. The combined rotational :forces of both gears will then be transmitted to the gear shaft H4, which is keyed to the gear |04 and which is journalled in the bushings ||5.

The pinion shaft H6, which is connected to the gear shaft H4 by the coupling will transmit the rotationalforce from the gears |03 and |04 to the spur gear I8 through the integral spur pinion I9 out thereon. The torque from the spur gear |18 is transmitted to the drive shaft |20 through the clutch hub |2| which is keyed and clamped thereon and which is held in engagement with the spur gear by the balls |22 being thrust outward into the drilled holes in the spur gear hub by the springs |23.

The drive shaft iii] is journalled in the pedestal |24 and gear cover |25, as in the pin-ion shaft |16. The seal |26 on the pinion shaft I6 prevents entrance of uid into the oil reservoir |21 in the pedestal |24 while the seal |28 prev-ents the escape of oil from the oil reservoir.

The position indication for the driven unit is shown on the top cover and dial plate |00 by the pointer 29, which is driven by the gear shaft i4 through appropriate gearing |30 and the speed reducer |31.

It will be noted that the coupling il? can be slipped upward and that a wrench can be slipped between the'gap between the gear and pinion shafts I4 and I6 to manually operate the drive shaft as an emergency measure in the event that the gear unit should be rendered inoperative because of lack of, or insufficient fluid pressure.

To reverse the direction of rotation the control lever 93 would be swung to the closeV position. This action would admit pressure throughv the triangular shaped port 99 to the passageway |32, whence it would be delivered to the space |33. Since the action of the pressure in this space upon the gears |03 and |04 would be the same as that previously described, except that the unbalance tooth area would be reversed,Y

Vit is evident that reversal of the direction of rotation would occur. ,n

'It will be noticed that the fluid iilling Ythe space between the gear teeth, which would have to be displaced upon reversal oi' the unit, is free to be displaced through the passageway |0i to the space |34 in the control valve 90, whence it can pass through the port |35 in the upper liner 9|. Since the space |36 above the gears |03 and |04 is in communication with the space Hi8 beneath the gears through the clearance around the gears and the cored holes |31, the displaced uid can be discharged through the drain pipe H0.

Since the two alternatives shown in Figs. 9 to 14 inclusive Iinvolve no change in function but only a change in structure of parts, it will be assumed that the foregoing description is applicable to their operation and that unless -parts are specically described as being difierent, they are identical.

On the first alternate, shown in Figs. 9 to 13 inclusive, the gear rims |38 and |39 are made of rubber or some rubber like compound; and are molded integral with a metal skeleton |40 to give them rigidity. The vertical members |4|, as well as the horizontal circular members |42, are perforated with holes |43, into which the resilient material flows during the vulcanization process to insure good bonding of the covering with the metal skeleton |40.

The skeleton is so constructed that the vertical and horizontal members would be interlocking, and the members welded together as a unit be fore the rubber covering is vulcanized thereon. it will be noted that the vertically extending members |4| are spaced around the periphery of the horizontal members |42 so as to form reinforcing members for each gear tooth. With this type of construction the only loads imposed upon the rubber are compression loads which are irnmediately transmitted to the rigid metal skeleton |40. Since the units arey keyed to the hub members |44 and |45, it is apparent that this embodiment will operate in the same manner as the embodiment previously described.

The alternate shown on Fig. 14 is the same as the one just described, except that metallic facings |46 with appropriate anchorage means are molded on the contacting surfaces of the gear teeth.

The purpose for the using of gears of a resilient material is this: in certain installations where water is the pressure medium for actuation of the drive unit, it may contain a rather high percentage of minerals in solution which tend to Vcollect on the surfaces with which it comes in contact. Since the clearances between the gear teeth must be qui-te close, it is evident that any appreciable scaling or encrustation on a solid metallic gear could and probably would so decrease the clearance that the gears would no longer operate but would jam. However, by using a. resilientforms, it will be obvious'to those skilled in the art Y Y u that it is not so limited, but is susceptible of various other changes and modifications, without departing from the spirit thereof, and I desire, therefore, that onlyV such limitations shall be placed thereupon as are specifically set forth in the appended claims. y.

What I claim is:

1. A gear adapted for use in hydraulic motors of the character described comprising a metallic skeleton framework having horizontal and vertical members secured together, said vertical members being spaced around the periphery of the framework to form reinforcing members for gear teeth, and a resilient material secured to the periphery of the framework to form teeth and intermediate grooves.

2. A gear according to claim l, in which the horizontal and vertical members are provided with pcrforations into which the resilient material enters, thereby to bond the resilient material mechanically to the framework.

3. A gear for use in hydraulic motors of the character described comprising a perforated metallic skeleton framework having horizontal and vertical members secured together, said vertical members being spaced around the periphery of the framework to form reinforcing members for gear teeth, a layer of resilient material forming teeth and intermediate grooves secured to the periphery of the framework and filling the perforations thereof, and a metallic covering bonded to said teeth and intermediate grooves.

4. A rotor for hydraulic motors of the gear type comprising a plurality of perforated disk members axially spaced with respect to each other,

about the framework filling the .perforations and forming a resilient periphery for the rotor bonded to the framework.

5. A rotor for hydraulic motors of the gear type comprising a plurality of axially spaced perforated disk members having radially extending notches therein spaced corresponding to the teeth of the rotor, perforated axially extending plates each having one edge fitting into corresponding notches in the plates, said disk members and plates forming a skeleton framework for the rotor, and a plastic resilient material molded4 a plurality of perforated axially extend-ing plates cooperating with the disk membersand radially spaced with respect to each other and forming j with the disk members a skeleton framework for the rotor, and a plastic resilient material molded 

